Lubricant measuring valve for centralized lubricating system



April 24, 1956 D. C. PETERSON ET AL LUBRICANT MEASURING VALVE FOR CENTRALIZED LUBRICATING SYSTEM Filed Aug. 17, 1950 5 Sheets-Sheet l amm, w

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Apnl 24, 1956 D, c. PETERSON ETAL 2,742,978

LUBRICANT MEASURING VALVE FoP` CENTRALIZED LUBRICATING SYSTEM Filed Aug. 17, 1950 5 Sheets-Sheet 2 April 24, 1956 D. 'QPETERsoN l-:TAL 2,742,978

LUBRICANT MEASURING VALVE FOR CENTRALIZED .LUBRICATING SYSTEM Filed Aug. 17, 1950 5 Sheets-Sheet 3 LUBRICANT MEASURNGv VALVE FOR CEN- TRALIZED LUBRICATNG SYSTEM David C. Peterson and Joseph C. Bystricky, Chicago, lll., assignors to Stewart-Warner Corporation, Chicago, Ill., a corporation of Virginia Application August 17, 1950, Serial No. 180,048

1 Claim. (Cl. 184-7) Our invention relates generally 'to lubricant measuring or feeder valves adapted for use as parts of centralized lubricating systems.

In the past most commercially used measuring or feeder valves for centralized lubricating systems have been constructed with valves and piston orl plunger parts which had toV4 be accurately fitted. The..productionmethods employed included not only machining but grinding and lapping operations. Itl was necessary kto have veryaccurate close fits between the parts to prevent leakage of lubricant and otherwise to insure satisfactory operation l improved measuring valve for centralized lubricating systems which may be machined from bar stock and which may be quickly and easily assembled by relatively unskilled labor and will nevertheless operate satisfactorily overalong period of time. z

Other objects will appear from the following description, reference being'had to the accompanying drawings, inwhichz Fig. 1 is a diagrammatic representation' of a portion of a centralized lubricating system of the single supplylline type; l t

Fig. 2 is an elevational view and Fig. 3 =is asplanview of an improved measuring or feeder valve usable as a part of the single line system shown in Fig. l;

Fig. 4 is an enlarged central vertical cross-sectional'view taken on the line 4-4 of-Fig. 3; l

Fig. 5 is a diagrammatic representation of a second type y of lubricating system, namely, a two-line system in which lubricant under pressure is alternately supplied to the two lines while the other line is vented;

Fig. 6 is an enlargedy vertical longitudinal sectional view taken on the plane of the line 6-6 of Fig'. 7 showing a valve usable in the two-line system of Fig. 5; y a

Fig. 7 is a sectional View taken on thelline 7-7` of Fig. 6; v p. .1

Fig. 8 is a central vertical sectional View of a modified form of the measuring valve shown in Fig. 4; and

Fig. 9 is a fragmentary sectional view of a modified form of inlet and outlet valve structure for use in the measurin valve shown in Figs. 6 and 7. y t i Referring to. Fig. l, the single supply line lubricating system comprises a lubricant reservoir 10y from which lthe lubricant is Withdrawn by a pumpv 12 and suppliedunder pressure to a conduit 14 at periodic intervals determined reither manually or by a suitable timing and operating mechanism 16. During the intervalthatflubricant under, v'pressure is not being supplied to the conduit 14,v thelatter y 2,742,978 Patented' Apr. 24,A 1956 ICC is vented to the lubricant reservor, and hencevsubstantially to atmospheric pressure, by rotation of a two-way valve 18 clockwis`e-90 from theposition` in which it issh'own in Fig. l, the valve 18 being either manuallyjoperatedior operated-in suitable timedsequence by the timing and-'operating mechanism 16. A plurality of measuringo" eeder valves 20 are suitably connected to the conduit 14.1 The conduit connections are made through suitablebushings 22 which are brazed or otherwise suitably secured-toa generally cylindrical body 24 of eachfmeasuriiig-valve.

The-measuring'valve 20 at the end of thecondujt` 1401' any branch thereof, has one of its bushings 22-closedby a plug 26, as indicated in the lowermost measuring valve 20 shown in Fig. l. The body 24 is provided with a diametricall'y drilled passageway 28 which communicates with the' bushings' '22.

' As shown in Fig. 4, this passageway communicates with a lthat of the va1ve body 24 leaving a cynudricai wan 59 short cylinder 30 by va port 32. The lower end of the body has a central bore 34 which communicates throughapair of passageways 3S with the inner end of a cylindrical bore 36 extending axially downward into the body V`A c'ap 40 is threaded to the lowerv end of the body 24 and 4is provided with a central portion42 having an outlet passageway 44 extending through it, the upper end of the 'passageway providing a seat 46 for an outlet valve 48 secured toor forming apart of the metal insert 50 of a cup-like piston 52. The lower-end of the passageway 44 jis preferably closed by a spring pressed ball check valve`54 and the cap 40 is provided with an externally threaded shank 56 for attachment to a bearing 58, or other part to be lubricated.

The piston v52 is preferably molded from a `synthetic rubber-like composition which will not deteriorate due to contact with lubricating oils and greases and 'the impurities which may be found therein. The piston 52'isfmolded around 'or is bonded to the insert plug 50 and'ha's' a ilarige portion 60 which resiliently engages and' seals against` the cylindrical wall of the short cylinder 30. This vflangeis suiiiciently soft and flexible that,up`on any substantial dilerence in pressure between the inlet port 30"ai1d the bore 34, `it or portions thereof will flex radially inwardly rto permit relatively free flow of lubricant from the inlet passageway 28 and port 32 to the'bore'34, and Ahence through passageways 38 to the lower endl of "the brei36. The diameter of'the bore 36 is substantially less'than of substantial radial thickness surrounding the bo're' to v'sustain the pressure of lubricant introduced into the bore through the passageways 38. n Moreover,`the' radial thicknes's of the body wall 59 encirclingy the bore 36 is suicient to provide a sturdy cylindrical shell I61 on the upper'end of the body 24 after enlargingthe outer end of the bore 36 by a downwardly extending counterbore 63. `Anan nular shoulder '90 formed by the body 24 at thelower end of the counterbore is spaced upwardly lfrom the'inner end of the bore 36. f i A piston 64 reciprocable in the bore 36 eoiriprises` a generally cylindrical metal stem'66 having alower prtion 68 of reduced diameter extending below'the`eounterbore 63 into the bore 36. lThe piston stem 66 forms a downwardly facing annular shoulder 65 at the upper end of the reduced diameter portion 68. A cylindrical sleeve 70, encircling the piston stern section 63'inabutting relation to the'shoulder 65, extends downward into theb'ore 36. The sleeve 70 is brazed or otherwise rigidly secured to the piston stem 66. A radial collar 67 integral. with "the end of thesleeve 70 adjacent the piston stem shoullend of the piston stern section 68 ,to provide aradially thin cylindrical space"y for `a' seal'l between'the piston stem.

and the adjacent cylindrical wallV of the bore 36. As shown, the diameter of the piston section 68 is substantially two-thirds that of the bore 36, thus minimizing the radial thickness of the structure used to prevent escape of lubricant past the piston stem.

., The packing around the stern vsection 68 includes. a metal backing ring 72 encirling the stern in abutting rela- Vtion tothe lower end of the sleeve v and having a fairly close t with the cylindrical wall of the bore 36. A second ring 74, which may be made of fiber, leather, or the like, and a flexible V-grooved annular packing ring 76 encircle the piston portion 68 successively belowthe-rst ring 72. The ring 76 isV preferably made of an oil or grease resistant synthetic rubberlike material.

/A relativelyheavy coil spring 78 is compressed between the collar 67 and the upper end of a cap` 80 screwed on the upper: end of the valve body `24. Thecap is centrally recessed to form an upward continuation of the counterbore6r3 in the valve body 24. The larger diameter of the Acounterbore 63 as `compared tothe bore 36 provides ampleA space for the spring 78 which should be of substantial size to provide the necessary downward force on the radial collar 67. It is noteworthy that the collar 67 together with the sleeve 70 form a cylindrical enlargement on the piston 66 which transmit downward force of the spring 78 to the piston stem and the packing encircling the lower end of the stem. The upper end of the stem 66 is provided with an axial bore 82 for the reception of a stroke adjusting stud 84 which is threaded in the cap 80 and may be locked in adjusted position .by a lock nut 86. In addition to serving as an upper limit stop for the stroke of the piston structure 64, the stud serves as a guide for the piston structure, maintaining it centralized in the cylindrical bore 36 and preventing canting thereof.

In the operation of the lubricating system shown in Figs. 1-4, the two-way valve 1,8 being in the position shown in Fig. 1, the pump 12 is operated to supply lubricant under pressure to the conduit system 14, and thus to the passageways 28 of the various measuring valves 20 which are connected to the conduit. Lubricant under pressure may flow from the passageways 28 through the port 32 of each measuring valve, thereby exerting pressure upon the upper `face of the piston 52 and forcing the latter downwardly a short distance to cause the ball check valve 48 tirmly to engage its seat 46 and thus close the outlet passageway 44.

Lubricant owing past the flange 60 of the piston 52 may tlow upwardly through the passageways 38 into the cylindrical bore 36 thereby pushing the piston 64 upwardly and compressing the coil spring 78. A charge of lubricant measured by the stroke of the piston structure 64, as great as permitted by the stroke adjusting stud 84, will thus be accumulated in the cylinder 36.

After all of the measuring valves 20 have thus been charged with the desired quantity of lubricant, the valve 18 is manually or automatically rotated clockwise through an angle of approximately thereby to connect the conduit 14 with a vent conduit 88, andpermitting the pressure in the conduit 14 to drop substantially'to atmospheric pressure. As this occurs, the spring pressed piston structure 64 of each of the various measuring valves will move downwardly under the action of its compressed coil spring 78 and thereby force the pistons 52 upwardly so as to cover and close their ports 32 and raise their valves 48 from the seats 46. Lubricant may then ow outwardlythrough the passageways 44 and past check valves 54 to the bearings 58. The downward motion of each of the piston structures 64 is limited by engagement of its anged collar 67 with the shoulder 90 at the base of the counterbore 63. Thus each bearing or other part to be lubricated is supplied with a charge of lubricant determined by the adjustment of its measuring piston stroke limiting stud 84.

l It will be noted that the stroke of the piston 52 is very short so that but a very minute quantity of lubricant need be returned to the conduit 14, and hence to the lubricant reservoir 10, at the time that the piston is moved upwardly to close the inlet port 32. However, the stroke of the piston 52 is sufficiently long to provide a passageway of adequate size between the ball valve 48 and its seat 46 when the valve is in open position.

In Figs. 5-7 there is disclosed a modified form of the invention in which the measuring valves are of the double acting type and are connected in a two-line system. ln Fig. 5 the system is shown as having a lubricant reservoir 10 from which lubricant is withdrawn and discharged by a pump 12 to either of two lubricant supply conduit lines and 101, depending upon the position of a ilowreversing valve 102, the latter, as well as the pump 12, being operated periodically either manually or by a tirning and operating mechanism 16 of any suitable construction. When the valve 102 is in the position shown, lubricant is pumped into conduit 100 and lubricant may ow from the conduit 101 through the vent pipe 88 to the reservoir. When the valve 102 is moved to position at right angles to that in which it is shown in Fig. 5, the flow from the pump is directed into conduit 101 and conduit 100 is vented to the reservoir through the vent pipe 88. A plurality of double` acting measuring valves 104 is suitably connected to the conduits 100 and 101 and may be connected by conduits 106 to bearings 108. Although only two measuring valves 104 are shown in Fig. 5, it will be understood that the illustrated valves are representative of practically any desired larger number of such valves which may be desired for a particular installation.

Referring more particularly to Figs. 6 and 7, each of the measuring valves 104 comprises a body or block 110 having a measuring cylinder 112 formed therein. A piston 114 having a metal center portion 116, provided at both sides with suitable packing rings 118, is freely reciprocable in the cylinder 112. Suitable connecting bushings are brazed or otherwise suitably secured to the body 110 and communicate with the passageway 122. An inlet port 124 leads from the passageway 122 to the upper end of a short cylinder 126 which extends to a counterbore 128. The counterbore 128 is threaded to receive a connecting fitting 130 to which the pipe or conduit leading to one of the bearings may be connected. This tting 130 includes an outlet valve seat 132 for a ball valve 134 formed at or secured to the end of the stem 136 which forms an insert for a piston 138 made of a suitable relatively soft flexible material such as a synthetic rubber compound which resists deterioration when in contact with oils and greases. The bore 128 intersects the enlarged end portion of the cylinder 112 to provide an inlet port 140 (Fig. 6). The conduit 101 is suitably connected to a passageway 142, which corresponds to the passageway 122, and has the same type of outlet and valve mechanism as shown in Fig. 7. for supplying lubricant to a bearing connected with fitting 131. The fitting 131 may be identical with fitting 130. The lubricant supplied through the passageway 142 tlows past a piston, identical with the piston 138, and may then flow into the left-hand (Fig. 6) end of the measuring cylinder 112 through an inlet port 144.

VThe left-hand end of the cylinder 112 is closed by a threaded plug 146, which also forms a stop engaged by the metallic portion of the piston 114 to limit the leftward stroke of the piston. The right-hand end of the cylinder 112 is closedbya hollow plug 148 which has a nut brazed or otherwise suitably secured therein for the reception of a stroke adjusting screw 152, the latter being clamped in adjusted position by a lock nut 154. It will be clear that upon removing the plug 148 the screw 152 may be adjusted to different positions to determine the stroke of the piston 114 and thus the quantity of lubricant discharged during each operating cycle. The body 110 is preferably provided with a pair of holes 156 and 157 for the reception of bolts or studs for the reception of a bolt by which a plurality of meas- .uring valve bodies may be secured together.

As-previously indicated, the lubricant under pressure is alternately supplied to the conduits100 and 101, `whilethe conduit not being supplied with lubricant is ventedto Vthe reservoir. For example, when lubricant under pressure is being supplied tothe conduit 100, it may iiow through passageway 122 andport124 to the short cylinder126 and "force thepiston 13,8downwardly toA bring the 4outlet valve 134 into firm engagement with its seat 132. Thereafter the rubber-like piston 138 will be Vdeformed suliciently to permit ow of lubricant past it through the port 140 into the right-hand end of the measuring cylinder 112, thereby forcing the piston 114 leftwardly to the position in which it is shown in Fig. 6, and thus discharging to the bearing, through the outlet fitting 131, the lubricant which was contained in the cylinder 112 to the left of the piston 114. A suitable time interval after all of the measuring valves 104 have thus been operated to supply measured quantities of lubricant to one of each of the pairs of bearings associated with the valves, the timing and operating mechanism 16 will become effective to render the pump 12 operative, and to reverse the position of the valve 102. The conduit 100 is thus vented to the lubricant reservoir while at the same time lubricant under pressure is discharged into conduit 101. In each of the measuring valves 124 the lubricant will then be supplied through its inlet port 144 to the left-hand end of the measuring cylinder 112, and the piston 114 will be forced rightward until arrested by engagement of the metal stem thereof with the head of the adjusting screw 152, meantime discharging th lubricant content to the right of the piston 114 to the bearing connected to the fitting 130. It will be under* stood that as soon as pressure develops beneath the piston 138, and the passageway 122 is vented to the reservoir, the piston 138 will be forced upwardly to the position in which it is shown in Fig. 7 and the valve 134 will therefore be raised from its seat 132 to permit liow of the lubricant from the right-hand end of the cylinder 112 to the bearing connected to the fitting 130.

In order to assure more reliable operation under ad verse conditions, the controlling piston and valve mechanism for the measuring valve of Figs. 5, 6 and 7 may be constructed in the manner shown in Fig. 9, in which reference characters of previously described elements have been applied to the corresponding parts. In this figure the fitting 130-a is provided with an inner extension 160 providing a loosely fitting guide for the stem portion of insert 162. The lower end of this insert is spherically shaped to provide an outlet valve 164, for engagement with a generally conical outlet valve seat 166. The extension 160 is provided with transversely drilled ports 168 to facilitate flow of lubricant past the valve 164 when the latter is unseated. The headed end 170 of the insert 162 tits snugly in a complemental cavity in the flexible piston 172.

The flange 174 of this piston is conformed so as yieldingly to engage the wall of the short cylinder 126 and to flex easily when lubricant under pressure is supplied through the inlet port 124. Since the stem of the insert 162 is guided by the extension 160, the possibility that the piston 172 might be distorted and displaced from its operative position, under adverse conditions of lubricant viscosity and pressure, is avoided.

For use under adverse operating conditions the measuring valve of Figs. 1-4 may be constructed in the manner shown in Fig. 8, in which the body 180 has a bore 182 for a piston structure 184. The piston structure comprises a generally cup-shaped metal body 186, guided in the bore 182, and having a suitable packing consisting of a backing washer 187 of leather or the like, and a V-ring 188, preferably of a suitable synthetic rubber compound. A piston stem 190, the lower end of which is of reduced diameter, `iits freelyinto the .cup-shaped, body,.186 :and

.normally abuts against the bottom thereof. .The upper end of the stem 190 is provided with a bore.191 for the reception of a guiding and piston stroke llimiting stud.192 which is adjustably secured in the customarymannenina top cap 194 which: is threaded .to the .body 180. A,spring 196..is compressed between the. cap 19.4 and the metal washer 198 which normally is forced against rtheupper end of body -and abutsa shoulder 199 on the stem 190.-r

The body 180 is provided with an inlet passageway 128, inlet port 32, short cylinder 30, passageway 38, piston 52, insert S0, andvvalve 48,738 ,11'11" thegtpreviously .described embodiment... The seat for. the outletvalve 48 and the check valve 54 are formed at the ends of a tubular seat member 200. driven-into.- a complementary bore'in the lower cap 202... J..

The measuring valve shown in Fig. 8 operates in the manner of the embodiment of Figs. 1-4. It will be noted, however, that the piston structure 184 is free to align itself in the bore 182 and that the piston stem 190 is likewise self-aligning with respect to the stud 192. This is a desirable feature which is of advantage during manufacture and assembly of the valve, because the tolerances relative to concentricity of the various machined surfaces may be increased, and because it insures that the stem and piston structure will not bind due to irregular wear. 'Ihe piston 184 and stem 190 will therefore be freely reciprocable after extended use of the valve.

When lubricant under pressure ilows into the pressure accumulator cylinder 182 the upper end of the cup-shaped piston body 186 engages the washer 198 and the upward movement of the piston structure is resisted by the compressed spring 196 until such movement is limited by the adjustable stud 192, thereby accurately determining the charge of lubricant which will be supplied to the connected bearing upon relief of the pressure of the lubricant supplied to the measuring valve.

In the several forms of the invention the parts may be manufactured using customary commercial machine tool tolerances. None of the metal parts need t together with any high degree of accuracy because the seals between all relatively moving metal parts, with the exception of the outlet valves 48, 132 and 164, are elfected by engagement of the relatively soft iiexible rubber parts with the metal parts.

In all forms of the invention the measuring valves may be readily assembled by employing simple methods and tools. Most of the parts may be machined from bar stock on automatic screw machines with the result that the cost of manufacturing the valves is very low.

While we have shown and described several embodiments of the invention, it will be apparent to those skilled in the art that the invention may be embodied in numerous other forms, al1 coming within the scope of the claim which follows:

We claim:

A lubricant measuring and pressure accumulator device for use as a part of a measuring valve of a centralized lubricating system, comprising, in combination, means forming a body having a large diameter cylindrical recess formed at one end thereof and a smaller diameter cylindrical recess formed as a continuation of the large diameter recess at the inner end thereof, the body forming an annular shoulder at the juncture of the small diameter recess with the large diameter recess, a cylindrical piston stem in the larger diameter recess defining an inwardly facing shoulder thereon and having' a portion of reduced diameter extending from the shoulder into the smaller recess, a sleeve secured to the smaller diameter portion of said piston stem in abutting relation to the shoulder thereon, the sleeve having a radial collar thereon overlying the shoulder on the body to limit movement of the stern into the smaller diameter recess, the portion of the stem of reduced diameter being of suicient size to cover a large portion of the end area of the smaller diameter recess, a packing encircling the smaller .diameter end of the stern to form a seal between the latter and the smaller diameter recess, a cap secured to said body and having a cavity formed as a continuation of said larger recess, a coil spring enclosed within said `larger recess and continuation thereof with its ends bearing against said collar and said cap, an axial bore formed in the outer end of the piston stern, and a motion limiting and alignment stud adjustably positioned in said cap and extending slidably into the piston stem bore to limit outward motion of the stem.

References Cited in the le of this patent UNITED STATES PATENTS 8 Vincent Dec. 26, Moore Nov. 17, Ericson Iune 27, Spang Sept. 10, Davis Oct. 29, Rockwell Oct. 13, Hoof Sept. 12, Melichar Oct. 8, Maclndoe Feb. 2,

FOREIGN PATENTS France May 20, France Feb. 24, Switzerland Nov. 16, Switzerland Dec. 3, Switzerland Dec. 1, 

